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WO2002052171A1 - Transmission a rapport variable - Google Patents

Transmission a rapport variable Download PDF

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Publication number
WO2002052171A1
WO2002052171A1 PCT/US2001/050098 US0150098W WO02052171A1 WO 2002052171 A1 WO2002052171 A1 WO 2002052171A1 US 0150098 W US0150098 W US 0150098W WO 02052171 A1 WO02052171 A1 WO 02052171A1
Authority
WO
WIPO (PCT)
Prior art keywords
output
drive shaft
disk
shaft
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2001/050098
Other languages
English (en)
Inventor
James A. Cillessen
Delon L. Uncapher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2002052171A1 publication Critical patent/WO2002052171A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/16—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface
    • F16H15/18—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally
    • F16H15/20—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a conical friction surface externally co-operating with the outer rim of the member A, which is perpendicular or nearly perpendicular to the friction surface of the member B

Definitions

  • the present invention relates to a disk member and cone member in direct contact with one another with variable relative positioning providing a transmission with a finitely and variable ratio of input to output speed.
  • Gear ratios of vehicles are generally fixed to limited numbers of gears. These gears try to establish an ideal relationship between the input force of the motor and the speed of motion of the vehicle. Thus, at lower speeds, higher torque is applied to the driving axle while maximum speed is low; and at higher speed less torque is required but maximum speed is high. Maximum engine torque is usually constant while driving torque requirements vary greatly with speed and road topology.
  • U.S. Patent No. 3,747,424 describes a speed reducing gear having a frustoconical body acting as the reducing mechanism driving a horizontal output shaft.
  • a horizontally engaged input drive shaft (worm gear) can be moved along the gradiated surface of the frustoconical body to reduce the speed ratio between the input and output.
  • the invention requires a 90 degree angle between the input and output shafts making it awkward for a transmission shaft. It also requires a worm type interface for force transfer because the contact area of input to output would be very slight without a worm interface. It is also designed as a speed reducer.
  • U.S. Patent 5,525,119 discloses a mechanism for varying rotational speed between two rotary shafts. It employs an intermediate roller contacting two cones. Speed variation is employed by the position of the roller between the two oppositely mounted cones while the roller is under pressure against the surfaces of both cones.
  • U.S. Patent 4,161,890 discloses an improvement to the contact surfaces in preventing slippage between two substantially inelastic members that are in frictional engagement .
  • U.S. Patent 4,183,253 discloses a moveable power transfer wheel interconnecting a pair of dual cones. Movement of the transfer wheel between both sets of cones varies input/output speed ratio.
  • What is needed is a mechanism employing direct drive means while able to vary the input/output speed ratio with no intermediate contacting parts. What is also needed is a mechanism to have the transfer of power directly between an input and an output member.
  • the present invention resolves these problems.
  • the present invention provides an ability to vary speed directly between two members while providing direct power transfer with no intermediate parts .
  • the present invention also provides in-line drive. That is, the input shaft and output shaft can be maintained with their individual axis in a coplanar relationship.
  • the present invention is also simple to manufacture with minimal parts.
  • the present invention is also easily adjustable and maintainable.
  • the main aspect of the present invention is to provide a continuously variable speed (within set limits) between a driving shaft and a transmitting output shaft.
  • Another aspect of the present invention is to provide a means for input and output drive contacting surfaces to be in parallel for optimal power transfer. Another aspect of the present invention is to provide contact between both the driving member and the transmitting member in a co-linear fashion. That is, both members have outer surfaces that are maintained in parallel . Another aspect of the present invention is to provide a means of adjustment of the speeds. An axially moveable shaft coupled to the disk shaped member in a reciprocating fashion accomplishes this. Movement of the disk shaped member surface to various parts of the cone surface changes the speed ratio.
  • Another aspect of the present invention is to provide a means for insuring constant pressure between the surface of the disk member and the cone member during operation. Constant pressure and high frictional coefficients prevent slippage during operation.
  • Another aspect of the present invention is to provide a high coefficient of friction between the disk member and cone member when in operation.
  • Another aspect of the present invention is to provide a means of having the input and output drives along the same plane for ease of assembly in using applications such as automobiles for example.
  • Another aspect of the present invention is ease of manufacture via fewer parts than a standard transmission.
  • Another aspect of the present invention is improved reliability and life via fewer parts and fewer wear surfaces than a standard transmission.
  • Another aspect of the present invention is ease of maintainability.
  • Variable speed is accomplished by moving a disk shaped member along a conical shaped member.
  • the cone will be referenced as the input driving-member and the disk as the output-driving member.
  • the input driving member, or cone is connected to a shaft that is driven by a motor input such as an automobile engine. Both members are directly connected to input and output-drive shafts respectively and rotate along the axis of each shaft. Both members are in direct pressure contact with each other with no intermediate parts; thus power is transferred directly between the disk and cone members.
  • the outer edge surface of the disk is parallel with the outer edge surface of the cone.
  • a 1:1 speed ratio for example, can be maintained when the output disk member circumference is at the large end of the input cone member with matching circumference.
  • the ratio With the output drive shaft connected to the disk member and the input shaft connected to the cone member, the ratio would be 1:1. If the disk were moved to the smaller circumference (l/10 th circumference of disk for example) end of the drive cone the ratio would be 10:1. More torque would be transmitted at the lower ratio. Selection of ratios would be a design requirement dependent and changeable via maximum and minimum circumferences of the cone.
  • Movement of a positioner shaft connected to the disk member accomplishes variable output speed changes. This movement adjusts the surface contact point between the disk member and the cone member. This provides a different surface contact point between the disk shaped member and the cone shaped member.
  • the different surface contact point of the disk outer surface onto the cone outer surface is related to a different outside circumference of the cone member and thus a different drive ratio.
  • the outside edge surface of the disk member is parallel to the outside longitudinal edge surface of the cone member. Movement and retention of position could be accomplished, for example, by an electrically driven screw shaft or by a hydraulic system to provide infinitesimal adjustment while also providing direct lateral holding power.
  • Constant pressure between the disk member and the cone member contact points can be maintained with various design methods. Shown herein is a method using a system with a pivot point hinge that places a downward pressure on the output shaft by means of a lever arm, adjustable spring and cams . Pressure over the range of movement of the contact surface points between the disk and cone members is thus both constant and can be easily adjusted based on design requirements.
  • a high coefficient of friction can be maintained between the outer surface of the cone member and the outer surface of the disk member with modern materials that provide a high frictional coefficient while exhibiting relatively little wear.
  • the working cone member is presently flame sprayed with stainless steel onto the steel base. Other materials such as specially developed ceramics, kevlar, carbide impregnated materials etc. also may be desirable depending on the application.
  • Disk member outside edge thickness design variation also provides a design means of increasing or decreasing contact surfaces between the disk and cone member surfaces.
  • FIG. 1 is a frontal corner perspective view of the variable ratio transmission 1000.
  • FIG. 2 is a side view of the pressure plate assembly 500.
  • FIG. 2A is a top view of the pressure plate assembly 500 connected to the output shaft 7.
  • FIG. 2B is side view of the pressure adjustment assembly 600.
  • FIG. 2C is a frontal view of pressure adjustment assembly 600.
  • FIG. 3 is a frontal perspective view of ratio positioner plate 17.
  • FIG. 3A is a side view of ratio positioner plate 17.
  • FIG. 4 is a side view of output roller drive 9 and output drive shaft 7.
  • FIG. 5 is a side view of output roller drive disk 9 and output drive shaft 7 connected to ratio positioner plate 17 and ratio positioner adjustment shaft 16.
  • FIG. 6 is a frontal corner perspective view of alternate embodiment of variable ratio transmission 700.
  • the preferred embodiment of the variable ratio transmission 1000 is made up of two basic assemblies.
  • the lower section is the Input Drive Shaft Assembly 3000.
  • the upper section is the Output Drive Shaft Assembly 2000.
  • the Input Drive Shaft Assembly (driving member) 3000 as seen in Fig. 1 consists of an Input Drive Shaft (driving shaft) 1 that is driven directly from a motor drive supply 3 power input (detail not shown) .
  • Input drive shaft 1 rotates about longitudinal drive axis R--R as seen in Fig. 1.
  • the power input could be, for example, an automobile motor.
  • a conical drive member (driving cone) 2 is rigidly connected to input drive shaft 1.
  • Input drive shaft 1 is physically connected to base mount (frame) 20 bearing clamps at either end by input drive shaft clamp-A 4 and input drive shaft bearing-A 5 at one end. The other end of input drive shaft 1 is clamped to base mount 20 by input drive shaft retainer-B 11 and with input drive shaft bearing-B 6. In this position, conical drive member 2 is power driven directly by a motor drive supply 3. Conical drive member 2 is a tapering body along outer edge surface (tapered drive surface) 23.
  • the output drive shaft assembly (driven member) 2000 is seen in Fig 1.
  • the main components of output drive shaft assembly 2000 are the output drive shaft ' (transmission shaft) 7 , the output roller drive disk 9, the adjustable pressure assembly (adjustable compression force assembly) 500 (seen detailed in Fig 2, 2A) and the ratio positioner assembly 15.
  • the output drive shaft 7 as seen in Fig. 1, 2A, 4, 5 is connected to base mount 20 at the two pressure plate-to-base frame pivot points 50.
  • Output drive shaft 7 rotates about longitudinal axis (transmission axis) S--S as seen in Fig. 1.
  • Output roller drive disk 9 is internally grooved and mounted to output drive shaft 7 which is a spline shaft. Contact between output roller drive disk 9 and conical drive member 2 create the output drive force.
  • Adjustable pressure assembly 500 maintains downward pressure (compression) between output roller drive 9 and conical drive member 2.
  • Fig. 2A shows adjustable pressure assembly 500.
  • Each of the two pressure plate lever arms 51 are connected to the base mount 20 at pressure plate-to-base frame pivot points (pivot mounts or hinge points) 50.
  • Each pressure plate lever arm 51 pivots about pressure-to-base frame pivot points 50 within pressure plate frame seating beds 57.
  • Each pressure plate lever arm 51 contain output shaft bearing holes 52 for acceptance of output drive shaft 7.
  • the other end of each pressure plate lever arm top surface 59 is in contact with the surface of cams (cam lever arms) 53.
  • Pressure rod 55 is rigidly connected to each cam 53.
  • Pressure rod (connecting rod) 55 is also connected to base mount 20 at either end via two base frame-to-pressure rod brackets 56. Pressure rod 55 is allowed to swivel within each of base frame-to-pressure rod brackets 56.
  • FIG. 2B, 2C show pressure adjustment assembly 600.
  • Rotational movement of the cams 53 is achieved by rotation of pressure adjustment bolt 63.
  • pressure adjustment spring 62 is compressed or decompressed accordingly.
  • pressure adjustment spring 62 applies more or less force against pressure adjustment lever arm (lever bar) 60.
  • Pressure adjustment lever arm 60 is rigidly connected to pressure rod 55 at pressure adjustment lever arm to pressure rod contact point 61. Movement of pressure adjustment lever arms 60 causes rotation of pressure rod 55 and thus each cam 53 rotates. This rotation applies more or less pressure to each of pressure plate lever arms 51 at each pressure plate lever arm top surface 59.
  • Speed changes to output drive shaft 7 are controlled by adjusting the position of output roller drive 9 along conical member outer edge surface 23. Movement of ratio positioner assembly (disk positioner) 15 as seen in Fig. 1,5 accomplishes this position adjustment. Movement of ratio positioner adjustment shaft 16 in a reciprocating manner moves ratio positioner plate (end plate) 17 accordingly.
  • Ratio positioner shaft adjustment input drive member 18 supplies power for movement and retention to ratio positioner plate 17.
  • Ratio positioner drive shaft retainer encasement 21 is connected to base mount 20 with ratio positioner to frame retention plate 25. Power from ratio positioner shaft adjustment input drive member 18, for example, can be supplied by an electrically driven screw shaft or by hydraulics for both positioning and retention.
  • Fig. 3, 3A illustrate ratio positioner plate 17.
  • Ratio positioner plate 17 has four ratio positioner plate retention holes 28 for mounting ratio positioner to frame retention plate 25; and two ratio positioner shaft plate retention bolts 19 to hold the two parts of ratio positioner plate 17 together at joining surfaces of ratio positioner plate 22.
  • Ratio positioner plate 17 has a ratio positioner plate grease fitting 27 which lubricates ratio positioner plate retention cavity 30 surfaces by supplying lubrication through channel 31.
  • Ratio positioner plate 17 also has retention interlock sleeve 32 that assembles between output roller drive outer retention sleeve 8 and output roller drive inner retention sleeve 10. Retention interlock sleeve 32 assembles into output roller retention cavity 33. When ratio postioner plate 17 is assembled onto output roller drive 9, retention interlock sleeve 32 fitting into output roller retention cavity 33 provides the means of movement of output roller drive 9 along conical member outer edge surface 23.
  • Speed ratios are accomplished by moving output roller drive 9 along conical member outer edge surface 23. It should be noted that other means of positioning could be incorporated.
  • variable ratio transmission can be designed at various ratios. As an example, if output roller drive 9 is moved to the large circumference conical member edge 26 and the circumferences of both are the same, then the ratio would be 1:1 and the output shaft 7 would rotate at the same speed as the input drive shaft 1. In automobiles, this may be a "high” gear. When output roller drive 9 is moved to the small circumference conical member edge 14, the circumference of the conical drive member 2 is smaller than the circumference of output roller drive 9. In this position, the output ratio may be 10:1 for example. This would be similar to a "low” gear. At the "low” gear point, more drive torque is supplied to output drive shaft 7.
  • variable ratio transmission 700 is shown in Fig. 6.
  • This specific alternate embodiment employs a different method of applying compression between output roller drive disk 9 and conical driver member 2.
  • Conical member outer edge surface 23 and output roller drive outer edge surface 24 are held in compression by output drive shaft compression bolts 72 and output drive shaft compression springs 73.
  • the amount of pressure (compression) exerted is adjustable by manual rotation of each output drive shaft compression bolt 72.
  • output drive shaft 7 is connected to the base mount 20 by output drive shaft clamp 70 and output drive shaft bearing 71 at each end.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Transmission (100) servant à faire varier en continu la vitesse de rotation entre un élément moteur et un élément mené, un arbre moteur rotatif (1) étant monté sur l'élément moteur, un cône moteur (2) étant accouplé avec l'arbre moteur (1), un ensemble arbre d'entraînement de sortie (7) comprenant, de plus, un disque d'entraînement de sortie à roulement (14) dont une surface périphérique est en contact par friction avec le cône (2), un positionneur de rapport (15) servant à positionner le disque d'entraînement de sortie à roulement dans la position désirée le long du cône (2), ce qui permet de transmettre une sortie de rapport variable à l'arbre d'entraînement de sortie.
PCT/US2001/050098 2000-12-27 2001-12-21 Transmission a rapport variable Ceased WO2002052171A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US09/749,350 US6524214B1 (en) 2000-12-27 2000-12-27 Variable ratio transmission
US09/749,350 2000-12-27

Publications (1)

Publication Number Publication Date
WO2002052171A1 true WO2002052171A1 (fr) 2002-07-04

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ID=25013363

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2001/050098 Ceased WO2002052171A1 (fr) 2000-12-27 2001-12-21 Transmission a rapport variable

Country Status (2)

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US (2) US6524214B1 (fr)
WO (1) WO2002052171A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012038991A1 (fr) * 2010-09-21 2012-03-29 Italycar S.R.L. Variateur de couple
US9743989B2 (en) 2010-09-21 2017-08-29 Intuitive Surgical Operations, Inc. Method and system for hand presence detection in a minimally invasive surgical system

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7665377B2 (en) * 2005-12-09 2010-02-23 Steven Harrelson Cone and idler continuously variable transmission
NL1031887C1 (nl) * 2006-05-25 2007-11-27 Arthur Van Moerkerken Traploos versnellingssysteem.
US7856902B2 (en) * 2006-07-28 2010-12-28 Turbo Trac Usa, Inc. Variable transmission
EP1999007B1 (fr) * 2006-12-01 2009-10-28 Cakir Aga Motorlu Tasitlar Sanayi Ve Ticaret Ltd. Transmission directe à vitesse variable
US7958799B1 (en) 2008-11-10 2011-06-14 Cillessen James A Brake for gear cone transmission
JP5644455B2 (ja) * 2010-12-09 2014-12-24 日産自動車株式会社 ローラ式摩擦伝動ユニット
US9970521B1 (en) 2016-02-26 2018-05-15 Rodney J. Cook and successors in trust Infinitely variable transmission
CN110227287B (zh) * 2019-06-20 2021-04-20 四川锦美环保股份有限公司 一种具有调速和排砂功能的旋流沉砂池
CN119062728A (zh) * 2024-10-21 2024-12-03 同济大学 一种轨道车辆宽范围频率动态减振器

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US3747424A (en) 1972-02-28 1973-07-24 Gourevitch J Variable speed reducer
FR2218005A5 (fr) * 1973-02-09 1974-09-06 Point Andre
US4161890A (en) 1977-09-06 1979-07-24 Caterpillar Tractor Co. Friction drive contact zone
US4183253A (en) 1977-02-07 1980-01-15 Domenic Borello Dual surface angular power transfer wheel traction nipping device
US5525119A (en) 1992-02-25 1996-06-11 Marques; Jesus Mechanism for gradually and smoothly varying rotational speed between a drive member and a driven member

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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE314836C (fr) *
GB144380A (en) * 1919-03-10 1920-06-10 Charles Frederick Beauvais Improvements in or relating to friction driving mechanism for motor road and other vehicles
US3747424A (en) 1972-02-28 1973-07-24 Gourevitch J Variable speed reducer
FR2218005A5 (fr) * 1973-02-09 1974-09-06 Point Andre
US4183253A (en) 1977-02-07 1980-01-15 Domenic Borello Dual surface angular power transfer wheel traction nipping device
US4161890A (en) 1977-09-06 1979-07-24 Caterpillar Tractor Co. Friction drive contact zone
US5525119A (en) 1992-02-25 1996-06-11 Marques; Jesus Mechanism for gradually and smoothly varying rotational speed between a drive member and a driven member

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012038991A1 (fr) * 2010-09-21 2012-03-29 Italycar S.R.L. Variateur de couple
US9243693B2 (en) 2010-09-21 2016-01-26 Italycar S.R.L. Speed variator
US9743989B2 (en) 2010-09-21 2017-08-29 Intuitive Surgical Operations, Inc. Method and system for hand presence detection in a minimally invasive surgical system

Also Published As

Publication number Publication date
US6524214B1 (en) 2003-02-25
US6997848B1 (en) 2006-02-14

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